Office Action 1: Non-Final Rejection (2025-03-19)
Rejection types: 103 - Obviousness, 112 - Written Description/Enablement

CLAIMS:
Amendments to the Claims:

This listing of claims will replace all prior versions and listings of claims in the application.

Listing of Claims:

1\. (Currently Amended) A compensation mechanism for a displacement machine according to the spiral principle, in particular a scroll compressor, wherein the compensation mechanism has a driveshaft with a center axis \[\[S\]\] and a compensation device , which:\[\[-\]\] has a cylindrical hub element that is mounted on a first eccentric pin of the driveshaft so that it can rotate around an axis of rotation \[\[P\]\], and
\[\[-\]\] a compensation element , which is mounted on the hub element so that it can rotate around an axis of rotation \[\[J\]\], and has an eccentrically arranged slotted hole that extends in a radial direction in relation to the axis of rotation \[\[J\]\],
wherein a second eccentric pin of the driveshaft is guided in the slotted hole of the compensation element in such a way that a Scotch yoke is formed between the slotted hole an the axis of rotation \[\[J\]\] of the compensation element .
2\. (Currently Amended) The compensation mechanism according to The compensation mechanism according to
 wherein,a center of gravity of the compensation element has an oscillating component during operation, wherein the center of gravity oscillates around a connecting line \[\[JQ\]\] between the axis of rotation \[\[J\]\] of the compensation element and a center axis \[\[Q\]\] of the slotted hole .
3\. (Currently Amended) The compensation mechanism according to The compensation mechanism according to
 wherein,the center of gravity of the compensation element has a linear component during operation, wherein the center of gravity moves along the connecting line \[\[JQ\]\], and wherein the linear component is larger than the oscillating component.
4\. (Currently Amended) The compensation mechanism according to claim 1, wherein, the axis of rotation \[\[J\]\] of the compensation element is arranged concentrically to a center axis \[\[C\]\] of the hub element .

5\. (Currently Amended) The compensation mechanism according to claim 1, wherein, the axis of rotation \[\[J\]\] of the compensation element is arranged eccentrically to a center axis \[\[C\]\] of the hub element .

6\. (Currently Amended) The compensation mechanism according to claim 1, wherein, the hub element has an eccentric hub bore , in which the first eccentric pin of the driveshaft is arranged.

7\. (Currently Amended) The compensation mechanism according to claim 1, wherein, the compensation element has a reception bore , with which the compensation element is rotatably mounted on the hub element .

8\. (Currently Amended) The compensation mechanism according to claim 1, wherein, the compensation element has a guide section and an equalizing weight , wherein the equalizing weight extends in an arc around the guide section .
9\. (Currently Amended) The compensation mechanism according to The compensation mechanism according to
 wherein,the reception bore and the slotted hole are arranged in the guide section .

10\. (Currently Amended) The compensation mechanism according to claim 8 ,herein,the equalizing weight extends half-annularly around the axis of rotation \[\[J\]\] of the compensation element .

11\. (Currently Amended) The compensation mechanism according to claim 8, wherein, the guide section and the equalizing weight are designed as a single piece, in particular monolithically.

12\. (Currently Amended) The compensation mechanism according to claim 1, wherein, the first eccentric pin of the driveshaft has a larger diameter and/or a larger length than the second eccentric pin of the driveshaft .

13\. (Currently Amended) The compensation mechanism according to claim 1, wherein, the hub element protrudes along its center axis \[\[C\]\] over the compensation element , in particular the equalizing weight .

14\. (Currently Amended) The compensation mechanism according to claim 1, wherein, the hub element is rotatably mounted on the first eccentric pin of the driveshaft via a plain or needle bearing and/or that the compensation element is rotatably mounted on the hub element via a plain or needle bearing.

15\. (Currently Amended) A displacement machine according to the spiral principle, in particular a scroll compressor, with a compensation mechanism according to claim 1.

16\. (Currently Amended) The displacement machine according to The displacement machine according to
 wherein,the hub element carries a scroll bearing, which is connected with a movable, in particular operationally orbiting, displacement spiral, wherein the movable displacement spiral engages into a stationary displacement spiral.

OFFICE ACTION:
DETAILED ACTION
Notice of Pre-AIA  or AIA  Status
The present application, filed on or after March 16, 2013, is being examined under the first inventor to file provisions of the AIA .
Claim Objections
Claim 1 is objected to because of the following informalities:
Claim 1 recites “an the axis of rotation” in line 12 which should be changed to --the axis of rotation--. Furthermore, in lines 2-3, the claim recites “the compensation mechanism has” which should be changed to --the compensation mechanism comprising-- to provide proper transitional phrase to the claim distinguishing the preamble from the body. Additionally, in lines 4-5, the claim recites “a compensation device which: has” which should be changed to --a compensation device which includes:--.
Appropriate correction is required.
Claim Rejections - 35 USC § 112
The following is a quotation of 35 U.S.C. 112(b):
(b)  CONCLUSION.—The specification shall conclude with one or more claims particularly pointing out and distinctly claiming the subject matter which the inventor or a joint inventor regards as the invention.
The following is a quotation of 35 U.S.C. 112 (pre-AIA ), second paragraph:
The specification shall conclude with one or more claims particularly pointing out and distinctly claiming the subject matter which the applicant regards as his invention.
Claims 1-16 are rejected under 35 U.S.C. 112(b) or 35 U.S.C. 112 (pre-AIA ), second paragraph, as being indefinite for failing to particularly point out and distinctly claim the subject matter which the inventor or a joint inventor (or for applications subject to pre-AIA  35 U.S.C. 112, the applicant), regards as the invention.
Regarding claims 1, and 13, the phrase in particular renders the claims indefinite because it is unclear whether the limitation(s) following the phrase are part of the claimed invention.  See MPEP § 2173.05(d).
Claim Rejections - 35 USC § 103
In the event the determination of the status of the application as subject to AIA  35 U.S.C. 102 and 103 (or as subject to pre-AIA  35 U.S.C. 102 and 103) is incorrect, any correction of the statutory basis (i.e., changing from AIA  to pre-AIA ) for the rejection will not be considered a new ground of rejection if the prior art relied upon, and the rationale supporting the rejection, would be the same under either status.
The following is a quotation of 35 U.S.C. 103 which forms the basis for all obviousness rejections set forth in this Office action:
A patent for a claimed invention may not be obtained, notwithstanding that the claimed invention is not identically disclosed as set forth in section 102, if the differences between the claimed invention and the prior art are such that the claimed invention as a whole would have been obvious before the effective filing date of the claimed invention to a person having ordinary skill in the art to which the claimed invention pertains. Patentability shall not be negated by the manner in which the invention was made.
Claim(s) 1-16 is/are rejected under 35 U.S.C. 103 as being unpatentable over US 4,522,574 to Arai et al (Arai) in view of US 4,824,346 to Hiraga et al (Hiraga).
Regarding claim 1, Arai discloses a compensation mechanism for a displacement machine according to the spiral principle, in particular a scroll compressor (fig. 1), wherein the compensation mechanism has a driveshaft (7, figs. 1, 4) with a center axis S and a compensation device (14, figs. 1, 4), which:
has a cylindrical hub element (5, figs. 1, 4) that is mounted on a first eccentric pin (7B, fig. 4) of the driveshaft so that it can rotate around an axis of rotation P, and
a compensation element (14, fig. 4), which is mounted on the hub element so that it can rotate around an axis of rotation J, and has an eccentrically arranged second eccentric tab (16, fig. 4) that extends in a radial direction in relation to the axis of rotation J, wherein the tab is guided in a slotted hole (17A, fig. 4) of the driveshaft of the compensation element (40) in such a way that a Scotch yoke is formed between the slotted hole the axis of rotation J of the compensation element.
However, Arai does not explicitly disclose that the compensation element has an eccentrically arranged slotted hole that extends in a radial direction in relation to the axis of rotation J, wherein a second eccentric pin of the driveshaft is guided in the slotted hole  of the compensation element in such a way that a Scotch yoke is formed between the slotted hole the axis of rotation J of the compensation element.
Hiraga teaches in fig. 4 a eccentric pin (tab 155, fig. 4) on a shaft (15 fig. 4) and a corresponding hole (333, fig. 4) and discloses in col. 6, lines 56-65 that the hole and the tab for the compensation mechanism can be on bushing or the shaft. As such, the slotted hole and eccentric pin can be flipped to be on opposite parts.
Therefore, it would have been obvious to the one with ordinary skill in the art, before the effective filing date of the claimed invention, to have an eccentric hole in the compensation element and an eccentric pin in the shaft as disclosed by Hiraga in the device of Arai so as to achieve a compressor which holds a dynamic balance and, therefore, prevents vibration of the compressor (col. 2, lines 5-6).
Regarding claim 2, Arai combined with Hiraga discloses the compensation mechanism according to claim 1, wherein a center of gravity of the compensation element has an oscillating component during operation, wherein the center of gravity oscillates around a connecting line JQ between the axis of rotation J of the compensation element and a center axis Q of the slotted hole (operation of the compressor).
Regarding claim 3, Arai combined with Hiraga discloses the compensation mechanism according to claim 2, wherein the center of gravity of the compensation element has a linear component during operation (due to the shape of 333, fig. 5; Hiraga), wherein the center of gravity moves along the connecting line JQ, and wherein the linear component is larger than the oscillating component (due to the shape of 333, fig. 5; Hiraga).
Regarding claim 4, Arai combined with Hiraga discloses the compensation mechanism according to claim 1, wherein the axis of rotation J of the compensation element is arranged concentrically to a center axis C of the hub element (figs. 1, 4; Arai).
Regarding claim 5, Arai combined with Hiraga discloses the compensation mechanism according to claim 1, wherein the axis of rotation J of the compensation element is arranged eccentrically to a center axis C of the hub element (due to the shape of 333, fig. 5 there will be linear component to center of gravity crating eccentric axis to the center axis; Hiraga).
Regarding claim 6, Arai combined with Hiraga discloses the compensation mechanism according to claim 1, wherein the hub element has an eccentric hub bore (5, 15, fig. 4; Arai), in which the first eccentric pin of the driveshaft is arranged.
Regarding claim 7, Arai combined with Hiraga discloses the compensation mechanism according to claim 1, wherein the compensation element has a reception bore (through which 5, 10, 15 are installed, fig. 4; Arai), with which the compensation element is rotatably mounted on the hub element.
Regarding claim 8, Arai combined with Hiraga discloses the compensation mechanism according to claim 1, wherein the compensation element has a guide section (inner surface of 331, figs. 2, 5; Hiraga) and an equalizing weight (outer surface of 331, figs. 2, 5; Hiraga), wherein the equalizing weight extends in an arc around the guide section.
Therefore, it would have been obvious to the one with ordinary skill in the art, before the effective filing date of the claimed invention, to have the guide section and the equalizing weight as disclosed by Hiraga in the device of Arai so as to achieve a compressor which holds a dynamic balance and, therefore, prevents vibration of the compressor (col. 2, lines 5-6).
Regarding claim 9, Arai combined with Hiraga discloses the compensation mechanism according to claim 8, wherein the reception bore and the slotted hole are arranged in the guide section (fig. 5; Hiraga).
Regarding claim 10, Arai combined with Hiraga discloses the compensation mechanism according to claim 8, wherein the equalizing weight (outer surface of 331, figs. 2, 5; Hiraga) extends half-annularly around the axis of rotation J of the compensation element.
Regarding claim 11, Arai combined with Hiraga discloses the compensation mechanism according to claim 8, wherein the guide section and the equalizing weight (figs. 2, 5; Hiraga) are designed as a single piece, in particular monolithically.
Regarding claim 12, Arai combined with Hiraga discloses the compensation mechanism according to claim 1, wherein the first eccentric pin of the driveshaft has a larger diameter and/or a larger length than the second eccentric pin of the driveshaft (fig. 4, Arai; fig. 5; Hiraga).
Regarding claim 13, Arai combined with Hiraga discloses the compensation mechanism according to claim 1, wherein the hub element protrudes along its center axis over the compensation element, in particular the equalizing weight (fig. 4, Arai; fig. 5; Hiraga).
Regarding claim 14, Arai combined with Hiraga discloses the compensation mechanism according to claim 1, wherein the hub element is rotatably mounted on the first eccentric pin of the driveshaft via a plain or needle bearing (10, 15, fig. 4; Arai) and/or that the compensation element is rotatably mounted on the hub element via a plain or needle bearing (10, 15, fig. 4; Arai).
Regarding claim 15, Arai combined with Hiraga discloses a displacement machine according to the spiral principle, in particular a scroll compressor, with a compensation mechanism according to claim 1 (see rejection of claim 1 above).
Regarding claim 16, Arai combined with Hiraga discloses the displacement machine according to claim 15,  wherein the hub element carries a scroll bearing (10, 15, fig. 4; Arai), which is connected with a movable, in particular operationally orbiting, displacement spiral, wherein the movable displacement spiral engages into a stationary displacement spiral (figs. 1, 4; Arai).
Conclusion
The prior art made of record and not relied upon is considered pertinent to applicant's disclosure.
US 11,655,819 to Ichise et al.
US 11,193,490 to Kuma et al.
US 10,400,771 to Valdez et al.
US 2010/0166589 to Iwano et al.
All references above describe general state of art.

APPLICANT REBUTTAL: Remarks Reconsideration is requested in view of the above amendments and the following remarks. Editorial amendments to the claims have been made to improve their form for US practice. No new matter is added.Claims 1-15 are pending.Claim 1 is objected to for the informalities noted. Claim 1 has been amended to address the objections. Withdrawal of the objection is requested.Claims 1-16 are rejected under 35 USC 112(b) as being unclear. Claims 1, 11, 13, 15 and 16 have been amended to delete the "in particular" language.The claims are definite. Withdrawal of the rejection is requested.Claims 1-16 are rejected under 35 USC 103 as being unpatentable over US 4522574 to Arai in view of US 4824346 to Hiraga. Applicant traverses.The combination of Arai and Hiraga does not teach or suggest a compensating element that has an eccentrically arranged slotted hole that extends in a radial direction relative to an axis of rotation of the compensating element, or a second eccentric pin of the driveshaft that is guided in the slotted hole of the compensation element in such a way that a Scotch yoke is formed between the slotted hole and the axis of rotation of the compensation element.One benefit of the claimed arrangement is a more direct connection of the compensation element to the driveshaft, since a disc according to Arai is dispensed with, and sealing between two displacement spirals of the displacement machine is improved.In addition, the more direct connection of the compensation element to the driveshaft means that vibrations within the displacement machine are reduced. This is due in particular to the fact that the slotted hole is formed in the compensation element and therefore the force is transmitted through the second eccentric pin via the wall of the slotted hole within the compensation element. This results in an improved oscillating and linear movement of the compensation element.Arai discloses a spiral compressor. Figure 1 of Arai is reproduced below showing the spiral compressor.2b
3b The Aai co   iss  a
pi nI1 i
T
i '9 AThe Arai compressor comprises a stationary spiral element 1 and an orbital spiral element 2 which form a compression mechanism. A balancing weight 14 is attached to the outer circumference of a hub 5 of the orbital spiral element 2 via a bearing 15. The balancing weight 14 has a key 16 that engages in a keyway 17A. For this purpose, a disc 17 is coupled to a crankshaft 7 of the compressor. See Figure 4 of Arai below.7dt In Arai, however, the keyway 17A, which is shown slotted, is not part of a compensation element such as the balancing weight 14. In Arai, the keyway 17A is formed in the disc 17 which is coupled or connected to the crankshaft 7. This is explicitly described in Arai at column 3, lines 29-35:A balancing weight 14 is secured to the outer periph- ery of the boss 5 of the orbital sgoll member 2 through 30 the medium of the bearing 15. The balance weight 14 has a key 16 which fits in a keyway 17A formed in a disc 17 coupled to the crankshaft 7. The key 16 is allowed to move in the radial direction along the keyway 17A.and in column 4, lines 15-20:produced as a result of the orbital movement and the 15 load produced by the pressure of the gas which is being compressed. On the other hand, the balancing weight 14, which engages through the key 16 and the keyway 17A with the disc 17 connected to the crankshaft 7 rotates together with the crankshaft 7, so as to rotate 20 together with the crankshaft 7, to thereby produce a In Arai, a direct and clear distinction is made between the disc 17 and the crankshaft 7, so that the disc 17 is not to be regarded as a component of the crankshaft 7 for this reason alone, but as a separate component which is attached to the crankshaft 7 in some manner not disclosed in Arai. At best, the keyway 17A is therefore provided in the separate disc 17 in Arai, but not on or in the crankshaft 7.In addition, in Arai, the key 16 is part of the balancing weight 14 and not the disc 17 and in no way to the crankshaft 7. Thus, in Arai, a Scotch yoke is not formed between a slotted hole of a compensation element and the axis of rotation of the compensation element.So Arai discloses a balancing mechanism which neither has a compensation element with an eccentrically arranged slotted hole, nor comprises a driveshaft with a second eccentric pin which is guided in the slotted hole in such a way that a Scotch yoke is formed between the slotted hole and the axis of rotation of the compensation element.Hiraga discloses two eccentric pins 154, 155 on the drive shaft (see Fig. 5).However, neither of the two eccentric pins 154, 155 is guided in a slotted hole of a compensation element in such a way that a Scotch yoke is formed between the slotted hole and an axis of rotation of the compensation element.For at least these reasons, claim 1 is patentable over the combination of Arai and Hiraga. Claims 2-16 depend from claim 1 and are patentable therewith for that reason alone and need not be separately distinguished at this time. Applicant does not concede the rejections to the dependent claims.Favorable reconsideration in the form of a notice of allowance is requested. Any questions concerning this paper can be directed to the attention of the undersigned at (612) 371-5349.Respectfully submitted, MERCHANT & GOULD, P.C.P.O. Box 2903 Minneapolis, Minnesota 55402-0903 (612) 332-5300 Dated: June 13, 2025

NEXT OFFICE ACTION: DETAILED ACTION
Notice of Pre-AIA  or AIA  Status
The present application, filed on or after March 16, 2013, is being examined under the first inventor to file provisions of the AIA .
Allowable Subject Matter
Claims 1-16 are allowed.
The following is an examiner’s statement of reasons for allowance:
Regarding claim , the closest prior art of record fails to disclose or render obvious the combination including:
“a second eccentric pin of the driveshaft is guided in the slotted hole of the compensation element in such a way that a Scotch yoke is formed between the slotted hole and the axis of rotation of the compensation element.”
Any comments considered necessary by applicant must be submitted no later than the payment of the issue fee and, to avoid processing delays, should preferably accompany the issue fee.  Such submissions should be clearly labeled “Comments on Statement of Reasons for Allowance.”
Response to Arguments
Applicant’s arguments, see Remarks, filed 6/13/2025, with respect to 103 rejection of claim 1 have been fully considered and are persuasive.  The 103 rejection of claim 1 has been withdrawn.
Conclusion

CITED REFERENCE SUMMARIES: Ref US11655819B2: Claims:
A scroll compressor comprising: a fixed scroll which includes a first end plate portion and a first swirl portion formed upright in the first end plate portion; an orbiting scroll which includes a second end plate portion having one surface facing the first end plate portion, a second swirl portion formed upright in the one surface of the second end plate portion and joining with the first swirl portion to form a compression chamber, and a boss portion formed on the other surface of the second end plate portion located opposite to the one surface and protruding from the other surface; a shaft which rotates about a first axis and which includes a first hole portion formed on close to one end surface of the shaft facing the other surface of the second end plate portion, the first hole portion extending in the direction of the first axis; a base seat portion which is integrally formed with the one end surface of the shaft so as to be protruded from the one end surface and which is provided with a press-fitting hole; a drive bush which includes a drive bush body formed between the second end plate portion and the one end surface of the shaft while being accommodated in the boss portion and is in contact with the one end surface, and a penetration portion penetrating the drive bush body in a direction from the second end plate portion toward the one end surface of the shaft; and an eccentric shaft having a constant outer diameter and extending in a direction of a second axis parallel to the first axis, the eccentric shaft being disposed in the first hole portion, the press-fitting hole through which the first hole portion is exposed, and the penetration portion; wherein the penetration portion includes a first portion which is disposed close to the orbiting scroll and a second portion which is disposed close to the shaft, the second portion is communicated with the first portion, and a diameter of the second portion is larger than that of the first portion, wherein the eccentric shaft is fitted into the first hole portion and the first portion and is press-inserted into the press-fitting hole, and wherein the base seat portion is fitted onto an outer peripheral surface of the eccentric shaft and is disposed in the second portion with a gap interposed between the base seat portion and the drive bush body, and the gap extends in the direction of the second axis from a contact surface to which the drive bush body and the one end surface are contacted to a surface formed in a radial direction of the second portion.
a fixed scroll which includes a first end plate portion and a first swirl portion formed upright in the first end plate portion;
an orbiting scroll which includes a second end plate portion having one surface facing the first end plate portion, a second swirl portion formed upright in the one surface of the second end plate portion and joining with the first swirl portion to form a compression chamber, and a boss portion formed on the other surface of the second end plate portion located opposite to the one surface and protruding from the other surface;
a shaft which rotates about a first axis and which includes a first hole portion formed on close to one end surface of the shaft facing the other surface of the second end plate portion, the first hole portion extending in the direction of the first axis;
a base seat portion which is integrally formed with the one end surface of the shaft so as to be protruded from the one end surface and which is provided with a press-fitting hole;
a drive bush which includes a drive bush body formed between the second end plate portion and the one end surface of the shaft while being accommodated in the boss portion and is in contact with the one end surface, and a penetration portion penetrating the drive bush body in a direction from the second end plate portion toward the one end surface of the shaft; and
an eccentric shaft having a constant outer diameter and extending in a direction of a second axis parallel to the first axis, the eccentric shaft being disposed in the first hole portion, the press-fitting hole through which the first hole portion is exposed, and the penetration portion;
wherein the penetration portion includes a first portion which is disposed close to the orbiting scroll and a second portion which is disposed close to the shaft, the second portion is communicated with the first portion, and a diameter of the second portion is larger than that of the first portion,
wherein the eccentric shaft is fitted into the first hole portion and the first portion and is press-inserted into the press-fitting hole, and
wherein the base seat portion is fitted onto an outer peripheral surface of the eccentric shaft and is disposed in the second portion with a gap interposed between the base seat portion and the drive bush body, and
the gap extends in the direction of the second axis from a contact surface to which the drive bush body and the one end surface are contacted to a surface formed in a radial direction of the second portion.
The scroll compressor according to claim 1 , wherein the shaft includes a second hole portion which is formed close to the one end surface, wherein a third hole portion is formed in a portion of the drive bush body facing the second hole portion, wherein the scroll compressor further comprises a limit pin which extends in a direction of a third axis parallel to the first and second axes; and a rubber ring which is provided on an outer peripheral surface of the limit pin, wherein a part of the limit pin provided with the rubber ring is accommodated in the second hole portion so that the rubber ring comes into contact with an inner peripheral surface of the second hole portion, and wherein a remaining part of the limit pin is fitted into the third hole portion.
wherein the shaft includes a second hole portion which is formed close to the one end surface,
wherein a third hole portion is formed in a portion of the drive bush body facing the second hole portion,
wherein the scroll compressor further comprises a limit pin which extends in a direction of a third axis parallel to the first and second axes; and a rubber ring which is provided on an outer peripheral surface of the limit pin,
wherein a part of the limit pin provided with the rubber ring is accommodated in the second hole portion so that the rubber ring comes into contact with an inner peripheral surface of the second hole portion, and
wherein a remaining part of the limit pin is fitted into the third hole portion.
The scroll compressor according to claim 2 , wherein a center axis of the drive bush is parallel to the first axis, and wherein the second and third axes are disposed at positions passing through a line orthogonal to the center axis.
wherein a center axis of the drive bush is parallel to the first axis, and
wherein the second and third axes are disposed at positions passing through a line orthogonal to the center axis.
The scroll compressor according to claim 1 , wherein an annular diameter-reduced portion is formed in an outer peripheral surface of the drive bush body located close to the shaft, and wherein the scroll compressor further comprises a balance weight which includes a fitting penetration portion fitted to a portion of the drive bush in which the diameter-reduced portion is formed.
wherein an annular diameter-reduced portion is formed in an outer peripheral surface of the drive bush body located close to the shaft, and
wherein the scroll compressor further comprises a balance weight which includes a fitting penetration portion fitted to a portion of the drive bush in which the diameter-reduced portion is formed.
The scroll compressor according to claim 1 , further comprising: a bush radial bearing which is disposed between an inner peripheral surface of the boss portion and an outer peripheral surface of the drive bush body, wherein the bush radial bearing is a ball bearing, and wherein a material of the drive bush is cast iron.
a bush radial bearing which is disposed between an inner peripheral surface of the boss portion and an outer peripheral surface of the drive bush body,
wherein the bush radial bearing is a ball bearing, and
wherein a material of the drive bush is cast iron.
The scroll compressor according to claim 1 , further comprising: a motor which is disposed outside the shaft and rotates the shaft; and a shaft radial bearing which rotatably supports an outer peripheral surface of a portion of the shaft located between the motor and the drive bush, wherein an outer diameter of the base seat portion is smaller than an inner diameter of the shaft radial bearing.
a motor which is disposed outside the shaft and rotates the shaft; and
a shaft radial bearing which rotatably supports an outer peripheral surface of a portion of the shaft located between the motor and the drive bush,
wherein an outer diameter of the base seat portion is smaller than an inner diameter of the shaft radial bearing.
Ref US11193490B2: [content unavailable]
Ref US10400771B2: Claims:
An eccentric compensating torsional drive system for reducing the rotational eccentric conflict as between multiple eccentric rotational movement limits on the eccentric offset within the drive system, said eccentric compensating torsional drive system comprising: (a) a motor for creating rotational motion about a first rotational axis; (b) a coupling having a primary end portion and an opposing secondary end portion, said primary end portion rotationally connected to the motor for creating rotational motion about the first rotational axis, the secondary end portion having an output shaft about a second rotational axis, the second rotational axis parallel to the first rotational axis and offset from the first rotational axis by a first offset distance; (c) an offset bearing having a proximal rotational axis and a parallel positioned distal rotational axis, the proximal rotational axis and the distal rotational axis offset from one another by a second offset distance, the offset bearing also having a first end portion and an opposing second end portion wherein the proximal and distal axes both span therebetween, the offset bearing further having an outer perimeter that is positioned about the distal axis and an inner perimeter that is positioned about the proximal axis, wherein the inner perimeter is disposed within the outer perimeter and is slidably engaged to the output shaft; (d) a dynamic element having a first dynamic axis and a first aperture that is positioned about the first dynamic axis, the first aperture slidably engaged to the offset bearing outer perimeter, the dynamic element also having a second aperture that is positioned a second dynamic axis, wherein the first and second dynamic axes are parallel to one another; (e) a static element having a first static axis and a third aperture that is positioned about the first static axis, wherein the first and second dynamic axes are parallel to the first static axis; and at least one bearing assembly for creating the first offset distance rotationally as between the second dynamic axis via the second aperture and the first static axis via the third aperture, wherein operationally the dynamic element moves in relation to the static element in a rotational manner via the first offset distance as driven by the motor for creating rotational motion through the coupling, wherein the offset bearing can have relative rotational movement to the output shaft and the first aperture to lessen the dynamic conflict as between the first offset distance and the at least one bearing assembly for creating the first offset distance in the torsional drive system, as the offset bearing acts as a floating variance in rotational offset via the second offset distance changing a radial position about the proximal axis.
(a) a motor for creating rotational motion about a first rotational axis;
(b) a coupling having a primary end portion and an opposing secondary end portion, said primary end portion rotationally connected to the motor for creating rotational motion about the first rotational axis, the secondary end portion having an output shaft about a second rotational axis, the second rotational axis parallel to the first rotational axis and offset from the first rotational axis by a first offset distance;
(c) an offset bearing having a proximal rotational axis and a parallel positioned distal rotational axis, the proximal rotational axis and the distal rotational axis offset from one another by a second offset distance, the offset bearing also having a first end portion and an opposing second end portion wherein the proximal and distal axes both span therebetween, the offset bearing further having an outer perimeter that is positioned about the distal axis and an inner perimeter that is positioned about the proximal axis, wherein the inner perimeter is disposed within the outer perimeter and is slidably engaged to the output shaft;
(d) a dynamic element having a first dynamic axis and a first aperture that is positioned about the first dynamic axis, the first aperture slidably engaged to the offset bearing outer perimeter, the dynamic element also having a second aperture that is positioned a second dynamic axis, wherein the first and second dynamic axes are parallel to one another;
(e) a static element having a first static axis and a third aperture that is positioned about the first static axis, wherein the first and second dynamic axes are parallel to the first static axis; and
at least one bearing assembly for creating the first offset distance rotationally as between the second dynamic axis via the second aperture and the first static axis via the third aperture, wherein operationally the dynamic element moves in relation to the static element in a rotational manner via the first offset distance as driven by the motor for creating rotational motion through the coupling, wherein the offset bearing can have relative rotational movement to the output shaft and the first aperture to lessen the dynamic conflict as between the first offset distance and the at least one bearing assembly for creating the first offset distance in the torsional drive system, as the offset bearing acts as a floating variance in rotational offset via the second offset distance changing a radial position about the proximal axis.
An eccentric compensating torsional drive system according to claim 1 , further comprising a drive bearing that is disposed as between the outer perimeter and the first aperture to operationally further facilitate the offset bearing floating variance.
An eccentric compensating torsional drive system according to claim 2 , wherein the drive bearing is a ball bearing.
An eccentric compensating torsional drive system according to claim 3 , wherein a first tangential slidable engagement clearance is between the output shaft and the inner perimeter and a second tangential slidable engagement clearance is between the outer perimeter and an inner ring of the drive bearing, wherein the first tangential slidable engagement clearance is substantially one-hundred and twenty-five percent (125%) of the second tangential slidable engagement clearance.
An eccentric compensating torsional drive system according to claim 4 , wherein the first tangential slidable engagement clearance is substantially point eight-five percent (0.85%) of the inner perimeter.
An eccentric compensating torsional drive system according to claim 4 wherein the second tangential slidable engagement clearance is substantially point five percent (0.5%) of the outer perimeter.
An eccentric compensating torsional drive system according to claim 2 , wherein the offset bearing further includes a shoulder disposed on the outer perimeter first end portion, wherein the shoulder helps to axially retain the offset bearing along the distal axis.
An eccentric compensating torsional drive system according to claim 1 , wherein the second offset distance is substantially fifteen percent (15%) of the first offset distance.
An eccentric compensating torsional drive system on a scroll compressor for reducing the rotational eccentric conflict, comprising: (a) a motor for creating rotational motion about a first rotational axis, wherein the motor has a drive shaft; (b) a coupling having a primary end portion and an opposing secondary end portion, the primary end portion rotationally connected to the drive shaft about the first rotational axis, the secondary end portion having an output shaft that is positioned about a second rotational axis, the second rotational axis parallel to the first rotational axis and offset from the first rotational axis by a first offset distance; (c) an offset bearing having a proximal rotational axis and a parallel positioned distal rotational axis, the proximal rotational axis and the distal rotational axis offset from one another by a second offset distance, the offset bearing also having a first end portion and an opposing second end portion wherein the proximal and distal axes both span therebetween, the offset bearing further having an outer diameter that is positioned about the distal axis and an inner diameter that is positioned about the proximal axis, wherein the inner diameter is disposed within the outer diameter and is slidably engaged to the output shaft; (d) a dynamic compressor scroll element having a first dynamic axis and a first inside diameter that is positioned about the first dynamic axis, the first inside diameter slidably engaged to the offset bearing outer diameter, the dynamic compressor scroll member also having a plurality of second inside diameters that are each about one of a plurality of second dynamic axes, wherein the first and second dynamic axes are all parallel to one another; (e) a static compressor scroll element having a plurality of first static axes, the static compressor scroll element also having a plurality of third inside diameters that are each positioned about one of the plurality of first static axes, wherein the first and second dynamic axes, the first static axis, and the plurality of first static axes are all parallel to one another; and (f) a plurality of pivotal bearing assemblies each having opposing ends that are offset by the first offset distance and including a shaft having a dynamic end portion, a mid-portion having the first offset distance, and a static end portion, the dynamic end portion having a housing bearing that has a slip fit with the second inside diameter and the static end portion having a housing bearing that has a slip fit with the third inside diameter, wherein operationally the dynamic element moves in relation to the static element in a rotational manner via the first offset distance as driven by the motor for creating rotational motion through the coupling output shaft that is at the first offset distance that drives the offset bearing through the first inside diameter, wherein the offset bearing can have relative rotational movement to output shaft and the first inside diameter to lessen the dynamic conflict as between the first offset distance and the plurality of pivotal bearing assemblies in the torsional drive system as the offset bearing acts as a floating variance in rotational offset via the second offset distance changing a radial position about the proximal axis.
(a) a motor for creating rotational motion about a first rotational axis, wherein the motor has a drive shaft;
(b) a coupling having a primary end portion and an opposing secondary end portion, the primary end portion rotationally connected to the drive shaft about the first rotational axis, the secondary end portion having an output shaft that is positioned about a second rotational axis, the second rotational axis parallel to the first rotational axis and offset from the first rotational axis by a first offset distance;
(c) an offse
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